Dual frequency hub mounted vibration suppressor system

ABSTRACT

A vibration suppressor system includes an annular electric motor system which independently controls rotation of at least two masses about the axis of rotation to reduce in-plane vibration of the rotating system. A method of reducing vibrations in a rotary-wing aircraft includes independently controlling a relative angular position of a multiple of independently rotatable masses to reduce vibrations of a main rotor system.

RELATED APPLICATIONS

The present application is a divisional of prior U.S. patent applicationSer. No. 12/353,217, filed Jan. 13, 2009, which claims the benefit U.S.Provisional Application No. 61/070,097, filed Mar. 20, 2008. The '217and '097 applications are herein incorporated by reference in theirentirety.

BACKGROUND

The present disclosure relates to a vibration suppressor system.

Vibration suppression is often utilized to null vibrations associatedwith a rotating system. Such vibrations, when left unattenuated may leadto crew and structural fatigue and premature failure of systemcomponents. The vibrations may also be transmitted through adjacentsupport structure to other areas and systems remote from the vibrationsource. Consequently, it may be desirable to suppress these vibrationsproximal the vibration source.

One application which exemplifies vibration isolation/absorption is themain rotor system of a rotary-wing aircraft. Typically, the main rotorsystem includes a hub system which drives a plurality of rotor bladessubject to a variety of aerodynamic and gyroscopic loads. For example,as each rotor blade advances or retreats relative to the freestreamairflow, each rotor blade experiences a rise and fall of in-planeaerodynamic drag. Furthermore, as the tip of each rotor blade advanceswith each revolution of the rotor system, the relative velocity at theblade tip may approach supersonic Mach numbers. As such, variations mayoccur at various coefficients which define blade performance (e.g.,moment, lift and drag coefficients). Moreover, gyroscopic and Coriolisforces are generated which may cause the blades to “lead” or “lag.”These effects, as well as others, generate vibrations, which, if notsuppressed, are transmitted to the airframe, typically through the mainrotor gearbox mount structure.

Various vibration suppressor systems have been devised to suppressvibrations. Mast-mounted vibration isolators suppress or isolatein-plane vibrations at a location proximal to the source. Transmission,cabin or cockpit absorbers reduce vibrations at a location remote fromthe source.

Mast-mounted vibration isolators having a plurality of resilient arms(i.e., springs) extend in a spaced-apart spiral pattern between a hubattachment fitting and a ring-shaped inertial mass. Several pairs ofspiral springs are mounted to and equiangularly arranged with respect toboth the hub attachment fitting and the inertial mass so as to producesubstantially symmetric spring stiffness in an in-plane direction. Thespring-mass system, i.e., spiral springs in combination with thering-shaped mass, is tuned in the non-rotating system to a frequencyequal to N*rotor RPM (e.g., 4P for a four-bladed rotor) at normaloperating speed, so that in the rotating system the spring mass systemwill respond to both N+1 and N−1 frequency vibrations (i.e., 3P and 5Pfor a four-bladed rotor). N is the number of rotor blades.

While the spiral spring arrangement produces a relatively small widthdimension (i.e., the spiraling of the springs increases the effectivespring rate), the height dimension of each vibration isolator isincreased to react out-of-plane loads via upper and lower pairs ofspiral springs. This increased profile dimension increases the profilearea, and consequently the profile drag produced by the isolator. Thespiral springs must also be manufactured to relatively precisetolerances to obtain the relatively exact spring rates necessary forefficient operation. As such, manufacturing costs may be significant.Additionally, the weight of this device is very high, thus reducing theuseful payload of the helicopter. Furthermore, these vibration isolatorsare passive devices which are tuned to a predetermined in-planefrequency and cannot be adjusted in-flight to isolate in-plane loadswhich may vary in frequency depending upon flight regime.

Yet another general configuration of a mast-mounted vibration isolatoris referred to as a “bifilar.” Bifilars include a hub attachment fittingconnected to and driven by the rotorshaft with a plurality of radialarms which project outwardly from the fitting with a mass coupled to theend of each arm via a rolling pin arrangement. A pin rolls within acycloidally-shaped bushing to permit edgewise motion of each massrelative to its respective arm. The geometry of the pin arrangement incombination with the centrifugal forces acting on the mass (imposed byrotation of the bifilar) results in an edgewise anti-vibration force ata 4 per revolution frequency which is out-of-phase with the large 4 perrevolution (“4P”) in-plane vibrations of the rotor hub for a 4 bladedrotor system. The frequency of 4P is the frequency as observed in anonrotating reference system such as the airframe.

Pairs of opposed masses act in unison to produce forces which counteractforces active on the rotor hub. For the masses to produce the necessaryshear forces to react the in-plane vibratory loads of the rotor system,counteracting bending moments are also produced. These force couples mayimpose relatively large edgewise bending loads in the radial arms, andconsequently, the geometry thereof must produce the necessary stiffness(EI) at the root end of the arms. As such, these increased stiffnessrequirements result in relatively large and heavy bifilar arms.

While the bifilar system has proven effective and reliable, the weightof the system, nearly 210 lbs for one typical system, may be detrimentalto the overall lifting capacity of the aircraft. Furthermore, the pinmount for coupling each mass to the respective radial arm may requireperiodic removal and replacement, which may increase the DirectMaintenance Costs (DMC) of aircraft operations.

SUMMARY

A vibration suppressor according to an exemplary aspect of the presentdisclosure includes an annular electric motor system defined about anaxis of rotation of a rotating system, and a control system incommunication with the annular electric motor system to independentlycontrol rotation of at least two masses about the axis of rotation toreduce in-plane vibration of the rotating system.

A method of reducing vibrations in a rotary-wing aircraft main rotorsystem having N number of blades which rotate about an axis of rotationat a rotational speed of 1P such that the main rotor system produces NPvibrations according to an exemplary aspect of the present disclosureincludes independently rotating a multiple of independently rotatablemasses disposed about an axis of rotation defined by the main rotorsystem and controlling a relative angular position of the multiple ofindependently rotatable masses to reduce the NP vibrations of the mainrotor system.

BRIEF DESCRIPTION OF THE DRAWINGS

The various features and advantages of this disclosure will becomeapparent to those skilled in the art from the following detaileddescription of the currently disclosed embodiment. The drawings thataccompany the detailed description can be briefly described as follows:

FIG. 1 is a general perspective view of an exemplary rotary wingaircraft embodiment for use with the present disclosure;

FIG. 2 is a side sectional view of a helicopter main rotor, including amain rotor shaft having a vibration suppression system mounted to theupper mast or shaft extension member of the main rotor system;

FIG. 3A is a schematic perspective view of a vibration suppressor systemhaving adjacent annular stators;

FIG. 3B is a sectional view through the system of FIG. 3A along line3B-3B;

FIG. 3C is an expanded perspective view of a single mass which rotatesupon an annular stator;

FIG. 4A is a top view of another non-limiting embodiment of a vibrationsuppressor system;

FIG. 4B is a cross-sectional view taken along line 4B-4B in FIG. 4A;

FIG. 4C is a cross-sectional view taken along line 4C-4C in FIG. 4B;

FIG. 5A is another non-limiting embodiment of a vibration suppressorsystem with ring bearings that support disk-shaped eccentric masses;

FIG. 5B is a cross-sectional view taken along line 5B-5B in FIG. 5A;

FIG. 5C is a cross-sectional view taken along line 5B-5B in FIG. 5A ofanother non-limiting embodiment that radially compresses the vibrationsuppressor system by location of eccentric masses between the two ringbearings;

FIGS. 6A-6E are schematic top views of a vibration suppressor systemwith segmental propulsion;

FIG. 7A is another embodiment of the vibration suppressor system havingelectromagnets arranged around an inner ring;

FIG. 7B is a top view of another vibrating suppressor system havingelectromagnets arranged around an outer ring;

FIG. 8A is a schematic representation of a condition where the maximumforce is produced by one annular stator of the vibration suppressorsystem; and

FIG. 8B is a schematic representation of a condition where anintermediate force is produced by one annular stator of the vibrationsuppressor system; and

FIG. 8C is a schematic representation of a condition where a minimumforce is produced by one annular stator of the vibration suppressorsystem.

DETAILED DESCRIPTION OF THE DISCLOSED EMBODIMENT

FIG. 1 schematically illustrates a rotary-wing aircraft 10 having a mainrotor system 12. The aircraft 10 includes an airframe 14 having anextended tail 16 which mounts an anti-torque system such as a tail rotorsystem 18. The main rotor assembly 12 is driven about an axis ofrotation R through a main rotor gearbox (illustrated schematically atMRG) which is powered by one or more engines E. The main rotor system 12includes a multiple of rotor blades 20 mounted to a rotor hub 22. Therotor hub 22 is driven about the axis of rotation R by a main rotorshaft 24 which is driven by the main rotor gearbox MRG. Although aparticular helicopter configuration is illustrated and described in thedisclosed non-limiting embodiment, other configurations and/or machines,such as high speed compound rotary wing aircraft with supplementaltranslational thrust systems, dual contra-rotating, coaxial rotor systemaircraft, turbo-props, tilt-rotors and tilt-wing aircraft, will alsobenefit herefrom.

A vibration suppressor system 30 is mounted to the main rotor system 12for rotation therewith and may thereby be referred to as a hub mountedvibration suppressor (HMVS). Vibratory forces active on the main rotorsystem 12 are generated by a variety of factors, although the dominantvibrations originate from aerodynamic and/or gyroscopic forces generatedby each rotor blade 20.

A four bladed rotor system, for example, produces 3P vibratory loads,i.e., in a single revolution, the magnitude of the load vector variesfrom a minimum to a maximum value three times in the rotating frame ofreference. The 3P vibratory loads resolve into 4P vibration in anon-rotating frame of reference such as the airframe 14 due to theaddition of the 1P rotor rotational speed. In addition, 5P vibratoryloads are produced in a direction opposite the rotational direction ofthe main rotor system. The 5P vibratory loads also resolve into 4Pvibration in the non-rotating frame of reference due to the subtractionof the opposite 1P rotor rotational speed. While a variety of factorsinfluence the vibratory spectrum of a rotor system, such vibrations aregenerally a result of each rotor blade experiencing maximum lift whenadvancing and minimum lift when retreating. In another example, a sevenbladed rotor system—having 6P co-rotation and 8P counter-rotationalvibratory load resolve into a 7P vibration in the non-rotating frame ofreference such as the airframe 14.

Referring to FIG. 2, the vibration suppressor system 30 generallyincludes an annular electric motor system 32, a control system 34 and apower system 36. The controller can be included in the electric motorsystem 32 i.e. it is typically in the rotating system) The annularelectric motor system 32 may be contained within a housing 38 forrotation with the main rotor system 12. The annular electric motorsystem 32 in one non-limiting embodiment includes a first and secondannular stator 40A, 40B mounted within the housing 38. Each stator 40A,40B represents a primary analogous to a fixed portion of a linearelectric motor. The first stator 40A is defined about the axis ofrotation R to support a first set of masses MA1, MA2, which areindependently rotatable about the first stator 40A (also illustrated inFIG. 3A). The second stator 40B is defined about the axis of rotation Rto support a second set of masses MB1, MB2 which are independentlyrotatable about the second stator 40B (also illustrated in FIG. 3A). Thefirst stator 40A may be located adjacent the second stator 40B in astacked arrangement which facilitates a light weight and low profilearrangement which may be readily mounted atop the main rotor hub 22within the housing 38.

Alternatively, the first stator 40A and second stator 40B may be locatedin the non-rotating system, i.e., in under the main rotor gearbox MRG.In this non-limiting embodiment, the MA1, MA2 would rotate at 4P and MB1and MB2 would also rotate at 4P but in the opposite direction.

The control system 34 issues control signals to an amplifier 34A of theannular electric motor system 32 to control the rotational speed andrelative angular position of the masses MA1, MA2, MB1, MB2 of thevibration suppressor system 30. The power system 36 in one non-limitingembodiment may be the aircraft electrical bus, which delivers electricalpower created by a main rotor gearbox powered generator 44. The massesMA1, MA2, MB1, MB2 each represent an independent secondary analogous toa moving part of a linear electric motor. The control system 34 mayinclude a speed sensor 42 which senses the instantaneous rotationalspeed 1P of the main rotor shaft 24 to control the rotational velocityand relative angular position of each of the masses the masses MA1, MA2,MB1, MB2.

Although the speed sensor 42 in one non-limiting embodiment may be adedicated unit which directly measures the main rotor system 12 speed,the control system 34 may alternatively or additionally obtain the speedinformation from the generator 44 within the power system 36. Thegenerator 44 turns at a predefined speed relative to the main rotorsystem 12 and may, in one non-limiting embodiment include a 5 kVagenerator which provides a 115 volt, 400 Hz 3 phase potential togenerate power for the vibration suppressor system 30 as well as providethe main rotor system speed reference signal. The generator 44 ismechanically driven by the MRG such that the rotational speed of thegenerator is a fixed multiple of the main rotor NP frequency. Theelectrical phase of the generator voltage is a fixed multiple of thegenerator rotational speed. Thus, the electrical voltage phase signal isa reflection of the NP frequency. As the rotor speed and NP frequencyvary while in flight, the electrical voltage phase signal also variesand is perfectly slaved thereto, i.e. a fixed multiple of the main rotorspeed. This makes the voltage signal an effective reference signal thatwill exactly track main rotor system speed. Hence, the control system 34may use the phase information to issue the appropriate low power controlsignals to the amplifier 34A which issues high power signals to thevibration suppression system 30.

While the vibration suppressor system 30 may employ a control system 34with a predefined schedule or model of the vibrations, e.g., atprescribed rotor speeds, another non-limiting embodiment utilizes avibration sensing system 46 with at least one vibration feedback sensor48 for issuing vibration signals indicative of the vibrations (e.g.,amplitude, frequency and phase) at one or more locations within thefixed frame of reference, e.g., MRG, fuselage, cabin, or cockpit. Itshould be understood that the vibration sensing system 46 mayalternatively be integrated within the control system 34. The controlsystem 34 samples vibration levels at predefined intervals or rates toidentify a trend—positive (lower vibration levels) or negative (largervibration levels) such that as vibration levels change, the controlsystem 34 issues modified control signals the vibration suppressorsystem 30 until a combination of rotational speed and angular positionof the masses MA1, MA2, MB1, MB2 minimize vibratory loads in the mainrotor system 12.

Power may be transferred from the stationary system to the rotatingsystem via a slip ring 50 or the like. Only a small amount of additionalweight is required inasmuch as the slip ring 50 is typicallypre-existing in a rotary wing aircraft for other systems e.g., a rotorblade de-ice system. This slip ring 50 may also be used to communicatecontrol signals when the control system 34 is mounted in the airframe 14rather than on the main rotor system 12. Alternatively, the controlsystem 34 may be located within the vibration suppressor system 30 suchthat the power system 36 communicates power to the slip ring 50 then tothe control system 34.

Referring to FIG. 3A, one non-limiting embodiment of the vibrationsuppressor system 30 includes the first annular stator 40A, the secondannular stator 40B with respective masses MA1, MA2 and MB1, MB2 whichindependently transit therein. The first annular stator 40A and thesecond annular stator 40B include a multitude of electro-magnets 52A,52B arranged around each respective stator 40A, 40B. It should beunderstood that many different magnet configurations are possible, forexample, a continuous iron portion with wire wound slots powered by theamplifier 34A. The multitude of electro-magnets 52A, 52B receive powerfrom the amplifier 34A in response to the control system 34 toindependently drive the masses MA1, MA2, MB1, MB2. Masses MA1, MA2 inthis non-limiting embodiment operate to suppress 5P vibration such thatfor a rotor system 12 which operates at 1P of 4.3 Hz, the masses MA1,MA2 transit the first annular stator 40A at 21.5 Hz in a rotationaldirection opposite that of the main rotor system 12. Masses MB1, MB2 inthis non-limiting embodiment operate to suppress 3P vibration such thatfor a rotor system 12 which operates at 1P of 4.3 Hz, the masses MB1,MB2 transit the second annular stator 40B at 12.9 Hz in a rotationaldirection the same as that of the main rotor system 12. It should beunderstood that this non-limiting embodiment is for a four-bladed mainrotor system 12 and that other main rotor systems 12 as well as otherrotational systems will also benefit therefrom.

As the first and second annular stator 40A, 40B are mounted to the mainrotor system 12 for rotation therewith, the masses MA1, MA2, MB1, MB2need only be driven at five revolutions per cycle of the rotor system(for masses MA1, MA2) and at three revolutions per cycle in the oppositedirection (for masses MB1, MB2) to achieve the desired 4P frequency.That is, since the masses MA1, MA2, MB1, MB2 are, in the rotatingreference system of the main rotor system 12 which rotates at onerevolution per cycle (1P), the masses MA1, MA2, MB1, MB2 need onlyaugment the rotational speed by the difference (3P+1P) to achieve thenecessary 4P in the stationary reference system for masses MB1, MB2which rotate in the direction of the rotor system 12 and 5P−1P toachieve the necessary 4P in the stationary reference system for massesMA1, MA2 which rotate in a direction opposite of the rotor system 12.

The first annular stator 40A and the second annular stator 40B aregenerally of a channel shape in cross-section (FIG. 3B) such that therespective masses MA1, MA2 and MB1, MB2 are guided therein as well asare retained therein when the electro-magnets 52A, 52B are unpowered.That is, the first annular stator 40A and the second annular stator 40Bare shaped to retain the masses MA1, MA2, MB1, MB2 when centrifugalforce is unavailable.

Although only a single mass (e.g., mass MA1) will be described in detailherein, it should be understood that each of the masses MA1, MA2, MB1,MB2 may be generally alike in configuration. Furthermore, each of themasses MA1, MA2 and MB1, MB2 provide the desired xP suppression byproviding a particular mass—here the masses MA1, MA2 may weighapproximately one pound (1 lb.), while the masses MB1, MB2 may weighapproximately two and one half pounds (2.5 lbs.) for stators 40A, 40Bwith a radius of approximately one foot. It should be understood thatthese dimensions are for example only and various arrangements may beprovided in accordance with the present disclosure.

Referring to FIG. 3C, each of the masses MA1, MA2, MB1, MB2 in thisnon-limiting embodiment generally include a first wheel 54, a secondwheel 56, a truck 58 which supports the wheels 54, 56 and a conductor 60(FIG. 3C). The conductor 60 may be poles (permanent magnets) for abrushless electric motor embodiment or a conductive element for aninductive motor embodiment. Bearings 62 or the like may be utilized tosupport the wheels 54, 56 on the truck 58. Each truck 58 represents anindependent secondary analogous to the moving part of a linear electricmotor.

The truck 58 and/or the conductor 60 may provide the majority of themass to provide the required anti-vibration forces. Furthermore, eitheror both of the wheels 54, 56 may be utilized to carry the majority ofthe mass. For the non-limited embodiment where low bearing loads in thetruck 58 are desired, either or both of the wheels 54, 56 may operate asthe conductor, i.e. no separate conductive plate type conductor 60 needbe provided on the truck 58. The other wheel 56, 54 may thereby carrythe majority of the mass. That is, one wheel 54 is relatively light inweight and conductive to provide propulsion, while the other wheel 56 ofthe same truck 58 is heavy in weight to define the eccentric mass.

Referring to FIG. 4A, each of the masses MA1, MA2, MB1, MB2 in thisnon-limiting embodiment includes a first wheel 80, a second wheel 82 anda truck 84 which supports the wheels 80, 82 with a radial-orientedconductor 86 (FIG. 4B) formed in part by the truck 84. At least aportion of the truck 84 forms the conductor 86 which is acted upon by astator 88. Each stator 88 represents a primary analogous to a fixedportion of a linear electric motor. The stator 88 in this non-limitingembodiment is a wire wound slotted and laminated iron component.

Each of the masses MA1, MA2, MB1, MB2 represents the independentsecondary analogous to the moving part of a linear electric motor. Theconductor 86 may be manufactured of a conductive material such as copperor aluminum. In this non-limiting embodiment, the conductor 86 isoriented to be in-plane with the plane formed by the primary stator 88such that the wheels 80, 82 need not provide propulsion. The wheels 80,82 ride within an outer guide ring 90 (see FIGS. 4B and 4C). The truck84 may form and/or include a relatively significant mass M between thewheels 80, 82 (FIG. 4C).

Referring to FIG. 5A, each of the masses MA1, MA2, MB1, MB2 in thisnon-limiting embodiment are supported within an annular bearing 100A,100B formed within an outer bearing support 102. Each of the masses MA1,MA2, MB1, MB2 in this non-limiting embodiment includes a radial-orientedconductor 104A, 104B formed in part by a truck 106A, 106B. At least aportion of the truck 106A, 106B forms the conductor 104A, 104B which isacted upon by a stator 110 which represents the primary analogous to afixed portion of a linear electric motor.

Each truck 106A, 106B may form a relatively significant eccentric mass Mwhich is supported adjacent the annular bearing 100A, 100B (FIG. 5B).That is, each truck 106A, 106B forms an eccentric mass M which rideswithin the annular bearing 100A, 100B.

Alternatively, each truck 106A′, 106B′ forms an eccentric mass M whichis arranged between the annular bearing 100A, 100B (FIG. 5C). Thisarrangement locates the eccentric mass M in a more radial outboardposition which facilitates a lighter weight mass for an equivalentdiameter annular bearing 100A, 100B.

Referring to FIG. 6A, the two individual masses MA1, MA2 located on thefirst annular stator 40A and the two individual masses MB1, MB2 locatedon the second annular stator 40B (not shown) are independent controlledthrough primary sector power transmission. The sixty degree (60°)primarysectors in FIGS. 6A-6E facilitate the minimization of electroniccomponents required to independently control the motion of each of themasses MA1, MA2 and MB1, MB2. Although only the first annular stator 40Awith masses MA1, MA2 will be described in the examples herein, it shouldbe understood that each of the two individual masses MB1, MB2 located onthe second annular stator 40B—or additional annular stators—aregenerally alike in configuration and operation.

The primary sectors are independently commanded when only one mass MA1,MB1 overlap that primary sector. In this way, one secondary mass MA1 isdriven relative to the other mass MA2.

In the examples illustrated in FIGS. 6A-6E masses MA1, MA2 are closetogether; thus a large anti-vibration force is produced. At this instantthe primary sector 1 propels mass MA2 and the primary sector 6 propelsmass MA2 thus independently regulating the velocities of masses MA1,MA2. As the two masses MA1, MA2 move clockwise, their dimensionprecludes both masses MA1, MA2 from occupying the same primary sector atthe same time. Notice on subsequent Figures, that MAR2 departs sector 2before MA1 enters sector 2. This permits independent control of themotions of masses MA1, MA2. Notice that MA1 and MA2 can of any dimensionsince the positions of masses MA1, MA2 may be tracked with a sensorsystem and can not be entirely within the same primary sector at thesame time.

As the masses MA1, MA2 move around the first annular stator 40A, theprimary sectors which are at the same azimuth as the respective massesMA1, MA2 are selectively powered to control the respective masses MA1,MA2.

On occasion one of the masses MA1, MA2 may abridge two primary sectors(FIGS. 6B-6E) such that two primary sectors are powered and commanded tocontrol the motion.

Referring to FIG. 7A, each of the masses MA1, MA2, MB1, MB2 in thisnon-limiting embodiment generally include an independent wheel 64 inwhich the wheel 64 itself operates as the mass and the conductingsecondary with no truck whatsoever. This eliminates the need forbearings. Each wheel 64 may travel within an outer guide ring 66 and aninner guide ring 68 which define a respective groove 66′, 68′. The innerguide ring 68 may be formed of electromagnets 70 which both power eachwheel 64 as well as restrains each wheel 64 when not powered. It shouldbe understood that other electro-magnet system arrangement mayalternatively or additionally be utilized, e.g., the electro-magnetguide ring 70A may be the outer ring 66A (FIG. 7B).

In operation, the masses MB1, MB2 (FIGS. 8A-8C) are propelled by theelectro-magnets 52A within the annular stator 40B at a rotational speedgreater than the rotational speed of the main rotor system 12 andappropriately positioned to yield a load vector P1 which is equal andopposite to the load vector R1 produced by the main rotor system 12.This counteracting load vector P1 may be interpreted as a vector whichattempts to cancel or null the displacement of the main rotor system 12and rotor shaft 24.

FIGS. 8A-8C depict various operating positions of masses MB1, MB2.Masses MA1, MA2 operate in an analogous manner which therefore need notbe described in further detail. The vibration suppressor system 30controls the rotational speed of the masses MA1, MA2, MB1, MB2 toproduce a counteracting load of the correct magnitude and phase tosuppress vibrations.

Referring to FIG. 8A, the masses MB1, MB2 are essentially adjacent andact in unison to produce a maximum force vector P1MAX. It should beunderstood that bumpers or such like may be provided to minimize impactbetween each mass MB 1, MB2, which may occur during some operationalconditions.

Referring to FIG. 8B, the masses MB1, MB2 define a right angle (90degrees) therebetween thereby producing a force vector P1MAX/(sqrt(2))that is a fraction of the magnitude of the maximum force vector.

Referring to FIG. 8C, the masses MB1, MB2 are directly opposite (180degree separation) and are essentially opposing to cancel the vectorsproduced by each of the masses MB1, MB2 such that essentially zero netforce is generated at P1MIN.

The ability to independently vary the relative angular position of themasses is especially valuable in applications wherein the magnitude ofthe vibratory load active in/on the rotating system varies as a functionof operating regime or operating speed. In a rotary-wing aircraft, forexample, it is common to require the highest levels of vibrationisolation in high speed forward flight i.e., where the rotor blades areexperiencing the largest differential in aerodynamic loading fromadvancing to retreating sides of the rotor system. Consequently, it maybe expected that the vibration suppressor system 30 produce the maximumload vector P1MAX (FIG. 8A). In yet another example, it is anticipatedthat the lowest levels of vibration isolation would occur in a loiter orhovering operating mode, where the rotor blades are exposed to thegenerally equivalent aerodynamic and gyroscopic affects. Consequently,it may be expected that the vibration suppressor system 30 a minimalload vector P1MIN (FIG. 8C).

It should be understood that relative positional terms such as“forward,” “aft,” “upper,” “lower,” “above,” “below,” and the like arewith reference to the normal operational attitude of the vehicle andshould not be considered otherwise limiting.

Although particular step sequences are shown, described, and claimed, itshould be understood that steps may be performed in any order, separatedor combined unless otherwise indicated and will still benefit from thepresent disclosure.

The foregoing description is exemplary rather than defined by thelimitations within. Many modifications and variations of the presentdisclosure are possible in light of the above teachings. The disclosedembodiments of this disclosure have been disclosed, however, one ofordinary skill in the art would recognize that certain modificationswould come within the scope of this disclosure. It is, therefore, to beunderstood that within the scope of the appended claims, the disclosuremay be practiced otherwise than as specifically described. For thatreason the following claims should be studied to determine the truescope and content of this disclosure.

What is claimed is:
 1. A vibration suppressor system for reducingvibrations in a rotating system, comprising: an annular electric motorsystem provided about an axis of rotation of the rotating system, saidannular electric motor system including an annular bearing and a firstmass supported within said annular bearing, said first mass guided aboutsaid axis of rotation by said annular bearing, wherein said first massis eccentric, said first mass including a truck being at least partiallyconductive, said annular electric motor system further including astator axially spaced-apart, relative to said axis of rotation, fromsaid truck; a control system in communication with said annular electricmotor system to control rotation of said first mass about said axis ofrotation to reduce in-plane vibration of the rotating system; wherein asecond mass is supported within said annular bearing, and wherein saidsecond mass is eccentric; and wherein said control system independentlycontrols rotation of said first and second masses about said axis ofrotation.
 2. The system as recited in claim 1, wherein said first andsecond masses each include an eccentric mass positioned between saidannular bearing.
 3. The system as recited in claim 1, wherein said firstand second masses are configured to rotate about said axis of rotation,and wherein a majority of the mass of each of said first and secondmasses is radially disposed on one side of said axis of rotation.
 4. Thesystem as recited in claim 1, wherein said first and second masses eachinclude trucks, and wherein said trucks are eccentric.
 5. The system asrecited in claim 1, further comprising: a rotor system having an Nnumber of blades which rotates about an axis of rotation at a rotationalspeed of 1P, such that said rotor system produces NP vibrations; asensor system which senses the NP vibrations; and wherein said controlsystem is in communication with said sensor system, said control systemoperable to identify variations of the NP vibrations to control anangular velocity of each of said first mass and said second mass toreduce the NP in-plane rotor system vibrations.
 6. The system as recitedin claim 5, further comprising a generator driven by said rotor system.7. The system as recited in claim 6, wherein a phase of the voltage fromsaid generator provides a phase reference to said control systemindicative of a rotational speed of said rotor system.
 8. The system asrecited in claim 1, wherein said axis of rotation intersects said firstmass.
 9. A vibration suppressor system for reducing vibrations in arotating system, comprising: an annular electric motor system providedabout an axis of rotation of the rotating system, said annular electricmotor system including an annular bearing and a first mass supportedwithin said annular bearing, said first mass guided about said axis ofrotation by said annular bearing, wherein said first mass is eccentric,and wherein said axis of rotation intersects said first mass; and acontrol system in communication with said annular electric motor systemto control rotation of said first mass about said axis of rotation toreduce in-plane vibration of the rotating system; wherein a second massis supported within said annular bearing, wherein said second mass iseccentric, and wherein said axis of rotation intersects said secondmass; and wherein said control system independently controls rotation ofsaid first and second masses about said axis of rotation.
 10. The systemas recited in claim 9, wherein said first and second masses each includetrucks, and wherein said trucks are eccentric.
 11. The system as recitedin claim 10, wherein said axis of rotation intersects said trucks.
 12. Avibration suppressor system for reducing vibrations in a rotatingsystem, comprising: an annular electric motor system provided about anaxis of rotation of the rotating system, said annular electric motorsystem including an annular bearing and first and second massessupported within said annular bearing, said first and second massesguided about said axis of rotation by said annular bearing, wherein saidfirst and second masses are eccentric, said first and second masses eachincluding a truck which is at least partially conductive, said annularelectric motor system further including at least one stator axiallyspaced-apart, relative to said axis of rotation, from said trucks; acontrol system in communication with said annular electric motor systemto control rotation of said first and second masses about said axis ofrotation to reduce in-plane vibration of the rotating system; andwherein said first and second masses are disk-shaped and each spansubstantially an entirety of an inner diameter of said annular bearing.